8-speed transmission

ABSTRACT

The transmission has a plurality of members that can be utilized in powertrains to provide eight forward speed ratios and one reverse speed ratio. The transmission includes four planetary gear sets having five torque-transmitting mechanisms, three fixed interconnections and a grounded member. The powertrain includes an engine and torque converter that is continuously connected to at least one of the planetary gear members, and an output member that is continuously connected with another one of the planetary gear members. The five torque-transmitting mechanisms provide interconnections between various gear members, and the transmission housing, and are operated in combinations of three to establish at least eight forward speed ratios and at least one reverse speed ratio.

CROSS REFERENCE TO RELATED APPLICATIONS

This application claims the benefit of U.S. Provisional Application No.60/909,140, filed Mar. 30, 2007, which is hereby incorporated byreference in its entirety.

TECHNICAL FIELD

The present invention relates to a power transmission having fourplanetary gear sets that are controlled by five torque-transmittingdevices to provide eight forward speed ratios and one reverse speedratio.

BACKGROUND OF THE INVENTION

Passenger vehicles include a powertrain that is comprised of an engine,multi-speed transmission, and a differential or final drive. Themulti-speed transmission increases the overall operating range of thevehicle by permitting the engine to operate through its torque range anumber of times. The number of forward speed ratios that are availablein the transmission determines the number of times the engine torquerange is repeated. Early automatic transmissions had two speed ranges.This severely limited the overall speed range of the vehicle andtherefore required a relatively large engine that could produce a widespeed and torque range. This resulted in the engine operating at aspecific fuel consumption point during cruising, other than the mostefficient point. Therefore, manually-shifted (countershafttransmissions) were the most popular.

With the advent of three- and four-speed automatic transmissions, theautomatic shifting (planetary gear) transmission increased in popularitywith the motoring public. These transmissions improved the operatingperformance and fuel economy of the vehicle. The increased number ofspeed ratios reduces the step size between ratios and therefore improvesthe shift quality of the transmission by making the ratio interchangessubstantially imperceptible to the operator under normal vehicleacceleration.

Six-speed transmissions offer several advantages over four- andfive-speed transmissions, including improved vehicle acceleration andimproved fuel economy. While many trucks employ power transmissionshaving six or more forward speed ratios, passenger cars are stillmanufactured with three- and four-speed automatic transmissions andrelatively few five- or six-speed devices due to the size and complexityof these transmissions.

Seven-, eight- and nine-speed transmissions provide further improvementsin acceleration and fuel economy over six-speed transmissions. However,like the six-speed transmissions discussed above, the development ofseven-, eight- and nine-speed transmissions has been precluded becauseof complexity, size and cost.

SUMMARY OF THE INVENTION

The present invention provides an improved transmission having fourplanetary gear sets controlled to provide at least eight forward speedratios and at least one reverse speed ratio.

The transmission family of the present invention has four planetary gearsets, each of which includes a first, second and third member, whichmembers may comprise a sun gear, a ring gear, or a planet carrierassembly member, in any order.

In referring to the first, second, third and fourth gear sets in thisdescription and in the claims, these sets may be counted “first” to“fourth” in any order in the drawing (i.e., left to right, right toleft, etc.). Additionally, the first, second or third members of eachgear set may be counted “first” to “third” in any order in the drawing(i.e., top to bottom, bottom to top, etc.) for each gear set.

Each carrier member can be either a single-pinion carrier member(simple) or a double-pinion carrier member (compound). Embodiments withlong pinions are also possible.

A first interconnecting member continuously connects the second memberof the first planetary gear set with the third member of the thirdplanetary gear set.

A second interconnecting member continuously connects the first memberof the second planetary gear set with the third member of the thirdplanetary gear set.

A third interconnecting member continuously connects the first member ofthe third planetary gear set with the first member of the fourthplanetary gear set.

The first member of the first planetary gear set is continuouslyconnected with a stationary member (transmission housing/casing).

The input member is continuously connected with the second member of thefourth planetary gear set. The output member is continuously connectedwith the second member of the second planetary gear set.

A first torque transmitting device, such as a brake, selectivelyconnects the third member of the fourth planetary gear set with astationary member (transmission housing/casing).

A second torque transmitting device, such as a clutch, selectivelyconnects the third member of the first planetary gear set with thesecond member of the third planetary gear set.

A third torque transmitting device, such as a clutch, selectivelyconnects the second member of the first planetary gear set with thesecond member of the fourth planetary gear set.

A fourth torque transmitting device, such as a clutch, selectivelyconnects the third member of the second planetary gear set with thesecond member of the third planetary gear set.

A fifth torque transmitting device, such as a clutch, selectivelyconnects the third member of the second planetary gear set with thethird member of the fourth planetary gear set.

The five torque-transmitting mechanisms are selectively engageable incombinations of three to yield at least eight forward speed ratios andat least one reverse speed ratio. Each shift is a single transitionshift, and three overdrive ratios are provided.

A variety of speed ratios and ratio spreads can be realized by suitablyselecting the tooth ratios of the planetary gear sets.

The above features and other features and advantages of the presentinvention are readily apparent from the following detailed descriptionof the best modes for carrying out the invention when taken inconnection with the accompanying drawings.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 a is a schematic representation of a powertrain including aplanetary transmission in accordance with the present invention;

FIG. 1 b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 1 a; and

FIG. 1 c is a schematic representation of the powertrain of FIG. 1 adepicted in lever diagram form.

DESCRIPTION OF THE PREFERRED EMBODIMENT

Referring to the drawings, there is shown in FIG. 1 a a powertrain 10having a conventional engine and torque converter 12, a planetarytransmission 14, and a conventional final drive mechanism 16. The engine12 may be powered using various types of fuel to improve the efficiencyand fuel economy of a particular application. Such fuels may include,for example, gasoline; diesel; ethanol; dimethyl ether; etc.

The planetary transmission 14 includes an input member 17 continuouslyconnected with the engine 12, a planetary gear arrangement 18, and anoutput member 19 continuously connected with the final drive mechanism16. The planetary gear arrangement 18 includes four planetary gear sets20, 30, 40 and 50.

The planetary gear set 20 includes a sun gear member 22, a ring gearmember 24, and a planet carrier assembly member 26. The planet carrierassembly member 26 includes a plurality of pinion gears 27 rotatablymounted on a carrier member 29 and disposed in meshing relationship withboth the sun gear member 22 and the ring gear member 24.

The planetary gear set 30 includes a sun gear member 32, a ring gearmember 34, and a planet carrier assembly member 36. The planet carrierassembly member 36 includes a plurality of pinion gears 37 rotatablymounted on a carrier member 39 and disposed in meshing relationship withboth the ring gear member 34 and the sun gear member 32.

The planetary gear set 40 includes a sun gear member 42, a ring gearmember 44, and a planet carrier assembly member 46. The planet carrierassembly member 46 includes a plurality of pinion gears 47 mounted on acarrier member 49 and disposed in meshing relationship with both thering gear member 44 and the sun gear member 42.

The planetary gear set 50 includes a sun gear member 52, a ring gearmember 54, and a planet carrier assembly member 56. The planet carrierassembly member 56 includes a plurality of pinion gears 57 mounted on acarrier member 59 and disposed in meshing relationship with both thering gear member 54 and the sun gear member 52.

The planetary gear arrangement also includes five torque-transmittingmechanisms 80, 82, 84, 85 and 86. The torque transmitting device 80 is astationary type torque-transmitting mechanism, commonly termed a brakeor reaction clutch. The torque transmitting devices 82, 84, 85 and 86are rotating-type torque-transmitting mechanisms, commonly termedclutches.

The input member 17 is continuously connected with the planet carrierassembly member 56 of the planetary gear set 50. The output member 19 iscontinuously connected with the planet carrier assembly member 36 of theplanetary gear set 30.

The sun gear member 22 of the planetary gear set 20 is continuouslyconnected with the transmission housing 60.

A first interconnecting member 70 continuously connects the planetcarrier assembly member 26 of the planetary gear set 20 with the ringgear member 44 of the planetary gear set 40. A second interconnectingmember 72 continuously connects the sun gear member 32 of the planetarygear set 30 with the ring gear member 44 of the planetary gear set 40. Athird interconnecting member 74 continuously connects the sun gearmember 42 of the planetary gear set 40 with the sun gear member 52 ofthe planetary gear set 50.

A first torque transmitting device, such as brake 80, selectivelyconnects the ring gear member 54 of the planetary gear set 50 with thetransmission housing 60. A second torque transmitting device, such asclutch 82, selectively connects the ring gear member 24 of the planetarygear set 20 with the planet carrier assembly member 46 of the planetarygear set 40. A third torque transmitting device, such as clutch 84,selectively connects the planet carrier assembly member 26 of theplanetary gear set 20 with the planet carrier assembly member 56 of theplanetary gear set 50. A fourth torque transmitting device, such asclutch 85, selectively connects the ring gear member 34 of the planetarygear set 30 with the planet carrier assembly member 46 of the planetarygear set 40. A fifth torque transmitting device, such as clutch 86,selectively connects the ring gear member 34 of the planetary gear set30 with the ring gear member 54 of the planetary gear set 50.

As shown in FIG. 1 b, and in particular the truth table disclosedtherein, the torque-transmitting mechanisms are selectively engaged incombinations of three to provide at least eight forward speed ratios andat least one reverse speed ratio, all with single transition sequentialshifts, and including three overdrive ratios.

As set forth above, the engagement schedule for the torque-transmittingmechanisms is shown in the truth table of FIG. 1 b. The chart of FIG. 1b describes the ratio steps that are attained in the above describedtransmission. For example, the step ratio between the first and secondforward speed ratios is 1.53, while the step ratio between the reversespeed ratio and first forward ratio is −0.76.

Referring to FIG. 1 c, the embodiment of powertrain 10 depicted in FIG.1 a is illustrated in a lever diagram format. A lever diagram is aschematic representation of the components of a mechanical device suchas an automatic transmission. Each individual lever represents aplanetary gearset, wherein the three basic mechanical components of theplanetary gear are each represented by a node. Therefore, a single levercontains three nodes: one for the sun gear member, one for the planetgear carrier member, and one for the ring gear member. The relativelength between the nodes of each lever can be used to represent thering-to-sun ratio of each respective gearset. These lever ratios, inturn, are used to vary the gear ratios of the transmission in order toachieve appropriate ratios and ratio progression. Mechanical couplingsor interconnections between the nodes of the various planetary gear setsare illustrated by thin, horizontal lines and torque transmittingdevices such as clutches and brakes are presented as interleavedfingers. If the device is a brake, one set of the fingers is grounded.Further explanation of the format, purpose and use of lever diagrams canbe found in SAE Paper 810102, authored by Benford, Howard and Leising,Maurice, “The Lever Analogy: A New Tool in Transmission Analysis”, 1981,which is hereby fully incorporated by reference.

The powertrain 10 includes an input member 17 continuously connectedwith the engine 12, an output member 19 continuously connected with thefinal drive 16, a first planetary gear set 20A having three nodes: afirst node 22A, a second node 26A and a third node 24A; a secondplanetary gear set 30A having three nodes: a first node 32A, a secondnode 36A and a third node 34A; a third planetary gear set 40A havingthree nodes: a first node 42A, a second node 46A and a third node 44A;and a fourth planetary gear set 50A having three nodes: a first node52A, a second node 56A, and a third node 54A.

The input member 17 is continuously connected with the node 56A. Theoutput member is continuously connected with the node 36A. The node 22Ais continuously connected with the transmission housing 60.

The node 26A is continuously connected with the node 32A and 44A. Thenode 42A is continuously connected with the node 52A.

A first torque-transmitting device, such as brake 80, selectivelyconnects the node 54A with the transmission housing 60. A secondtorque-transmitting device, such as clutch 82, selectively connects thenode 24A with the node 46A. A third torque-transmitting device, such asclutch 84, selectively connects the node 26A with the node 56A. A fourthtorque-transmitting device, such as clutch 85, selectively connects thenode 34A with the node 46A. A fifth torque-transmitting device, such asclutch 86, selectively connects the node 34A with the node 54A.

To establish ratios, three torque-transmitting devices are engaged foreach gear state. The engage torque-transmitting devices are representedby an “X” in each respective row. For example, to establish reversegear, the brake 80, clutch 85 and clutch 86 are engaged. The brake 80engages the node 54A with the transmission housing 60. The clutch 85engages the node 34A with the node 46A. The clutch 86 engages the node34A with the node 54A. Likewise, the eight forward speed ratios areachieved through different combinations of clutch engagement as per FIG.1 c.

The powertrain 10 may share components with a hybrid vehicle, and such acombination may be operable in a “charge-depleting mode”. For purposesof the present invention, a “charge-depleting mode” is a mode whereinthe vehicle is powered primarily by an electric motor/generator suchthat a battery is depleted or nearly depleted when the vehicle reachesits destination. In other words, during the charge-depleting mode, theengine 12 is only operated to the extent necessary to ensure that thebattery is not depleted before the destination is reached. Aconventional hybrid vehicle operates in a “charge-sustaining mode”,wherein if the battery charge level drops below a predetermined level(e.g., 25%) the engine is automatically run to recharge the battery.Therefore, by operating in a charge-depleting mode, the hybrid vehiclecan conserve some or all of the fuel that would otherwise be expended tomaintain the 25% battery charge level in a conventional hybrid vehicle.It should be appreciated that a hybrid vehicle powertrain is preferablyonly operated in the charge-depleting mode if the battery can berecharged after the destination is reached by plugging it into an energysource.

While the best modes for carrying out the invention have been describedin detail, those familiar with the art to which this invention relateswill recognize various alternative designs and embodiments forpracticing the invention within the scope of the appended claims.

1. A multi-speed transmission comprising: an input member; an outputmember; first, second, third and fourth planetary gear sets each havingfirst, second and third members; a first interconnecting membercontinuously connecting said second member of said first planetary gearset with said third member of said third planetary gear set; a secondinterconnecting member continuously connecting said first member of saidsecond planetary gear set with said third member of said third planetarygear set; a third interconnecting member continuously connecting saidfirst member of said third planetary gear set with said first member ofsaid fourth planetary gear set; said first member of said firstplanetary gear set being continuously connected with a stationarymember; and five torque-transmitting devices for selectivelyinterconnecting said members of said planetary gear sets with astationary member or with other members of said planetary gear sets,said five torque-transmitting devices being engaged in combinations ofthree to establish at least eight forward speed ratios and at least onereverse speed ratio.
 2. The transmission of claim 1, wherein a first ofsaid five torque transmitting devices is operable for selectivelyconnecting said third member of said fourth planetary gear set with astationary member.
 3. The transmission of claim 2, wherein a second ofsaid five torque transmitting devices is operable for selectivelyconnecting said third member of said first planetary gear set with saidsecond member of said third planetary gear set.
 4. The transmission ofclaim 3, wherein a third of said five torque transmitting devices isoperable for selectively connecting said second member of said firstplanetary gear set with said second member of said fourth planetary gearset.
 5. The transmission of claim 4, wherein a fourth of said fivetorque transmitting devices is operable for selectively connecting saidthird member of said second planetary gear set with said second memberof said third planetary gear set.
 6. The transmission of claim 5,wherein a fifth of said five torque transmitting devices is operable forselectively connecting said third member of said second planetary gearset with said third member of said fourth planetary gear set.
 7. Thetransmission defined in claim 1, wherein one of said five torquetransmitting devices comprises a brake; and the others of said fivetorque transmitting devices comprise clutches.
 8. The transmission ofclaim 6, wherein said first, second and third members of said first,second, third and fourth planetary gear sets comprise a sun gear member,a planet carrier assembly member and a ring gear member, respectively.9. The transmission of claim 1, wherein said input member iscontinuously interconnected with said second member of said fourthplanetary gear set, and said output member is continuouslyinterconnected with said second member of said second planetary gearset.
 10. A multi-speed transmission comprising: an input member; anoutput member; first, second, third and fourth planetary gear sets eachhaving first, second and third members; said input member beingcontinuously interconnected with said second member of said fourthplanetary gear set; said output member being continuously interconnectedwith said second member of said second planetary gear set; said firstmember of said first planetary gear set being continuously connectedwith a stationary member; a first interconnecting member continuouslyconnecting said second member of said first planetary gear set with saidthird member of said third planetary gear set; a second interconnectingmember continuously connecting said first member of said secondplanetary gear set with said third member of said third planetary gearset; a third interconnecting member continuously connecting said firstmember of said third planetary gear set with said first member of saidfourth planetary gear set; a first torque transmitting deviceselectively connecting said third member of said fourth planetary gearset with said stationary member; a second torque transmitting deviceselectively connecting said third member of said first planetary gearset with said second member of said third planetary gear set; a thirdtorque transmitting device selectively connecting said second member ofsaid first planetary gear set with said second member of said fourthplanetary gear set; a fourth torque transmitting device selectivelyconnecting said third member of said second planetary gear set with saidsecond member of said third planetary gear set; a fifth torquetransmitting device selectively connecting said third member of saidsecond planetary gear set with said third member of said fourthplanetary gear set; and said torque-transmitting mechanisms beingengaged in combinations of three to establish at least eight forwardspeed ratios and at least one reverse speed ratio between said inputmember and said output member.
 11. A multi-speed transmissioncomprising: an input member; an output member; first, second, third andfourth planetary gear sets each having a sun gear member, planet carrierassembly member and ring gear member; said input member beingcontinuously interconnected with said planet carrier assembly member ofsaid fourth planetary gear set; said output member being continuouslyinterconnected with said planet carrier assembly member of said secondplanetary gear set; said sun gear member of said first planetary gearset being continuously connected with a stationary member; a firstinterconnecting member continuously connecting said planet carrierassembly member of said first planetary gear set with said ring gearmember of said third planetary gear set; a second interconnecting membercontinuously connecting said sun gear member of said second planetarygear set with said ring gear member of said third planetary gear set; athird interconnecting member continuously connecting said sun gearmember of said third planetary gear set with said sun gear member ofsaid fourth planetary gear set; a first torque transmitting deviceselectively connecting said ring gear member of said fourth planetarygear set with said stationary member; a second torque transmittingdevice selectively connecting said ring gear member of said firstplanetary gear set with said planet carrier assembly member of saidthird planetary gear set; a third torque transmitting device selectivelyconnecting said planet carrier assembly member of said first planetarygear set with said planet carrier assembly member of said fourthplanetary gear set; a fourth torque transmitting device selectivelyconnecting said ring gear member of said second planetary gear set withsaid planet carrier assembly member of said third planetary gear set; afifth torque transmitting device selectively connecting said ring gearmember of said second planetary gear set with said ring gear member ofsaid fourth planetary gear set; and said torque-transmitting mechanismsbeing engaged in combinations of three to establish at least eightforward speed ratios and at least one reverse speed ratio between saidinput member and said output member.